FOR NATURAL GAS ENGINES TO REDUCE NOx EMISSIONS

ABSTRACT

A chambered sparkplug carrier and a natural gas engine management system are provided for reducing NOx emissions of pre-chambered combustion natural gas engines. A method for retro-fitting a pre-chambered combustion natural gas engine with a chambered sparkplug is also described.

TECHNICAL FIELD

The present disclosure relates to emission reduction for natural gasengines and in particular to reducing NOx emissions.

BACKGROUND

To reduce the emissions of NOx (NO and NO₂) and to use the natural gasfuel with high efficiency, engine manufacturers developed spark ignitedreciprocating internal combustion engines (SI-RICE) that operated withvery lean air to fuel ratios. In a lean mixture of air and fuel, thereis more air present than necessary to fully combust the natural gasfuel. The presence of the excess air reduces the maximum temperatureduring the combustion period, which reduces the formation rate fornitrogen oxides (NOx). Nitrogen oxides in the atmosphere, under manyconditions, cause the formation of ozone, which is harmful to plant andanimal health. As a consequence, NOx emissions, or emission rates, arelimited by regulation in many jurisdictions. As air-fuel mixtures becomeleaner (more excess air) NOx emissions are reduced. However, as themixtures become leaner, the standard sparkplug is unable to reliablyignite the air-fuel mixtures.

To overcome this limitation a small pre-combustion chamber (PCC) isplaced in or adjacent to the combustion zone in the engine. The air-fuelmixture in the PCC is controlled separately from the main combustionchamber, such that the mixture is made richer than the main combustionzone mixture. This enables a standard sparkplug to reliably ignite themixture inside the PCC. As the mixture in the PCC expands, the hot,burning gases enter the main combustion chamber through several holes inthe PCC. These burning gases are then able to more readily ignite thelean mixture in the main chamber than the standard sparkplug by itself.These gases expelled from the PCC have a relatively higher NOxconcentration compared to the combustion products from the main chamber.The resulting NOx concentration in the exhaust gases comes from the sumof those produced in the PCC and the main combustion chamber. Since thePCC volume is only a few percent of the volume of the main chamber, theresulting NOx concentration is lower than can be achieved without a PCC.

Additional apparatus, including a gas admission valve and a separatefuel delivery apparatus such as the check valve and fuel regulator forthe PCC as shown in FIG. 1, is required to ensure a richer air-fuelmixture in the PCC. The gas admission valve can fail to operatecorrectly and the PCC fuel delivery control can go out of adjustment,which requires engine adjustment or shutdown and gas admission valvereplacement. To eliminate the need for a separate fuel system, PCCsusing a standard sparkplug were designed to operate with the mainchamber air-fuel mixture.

Some manufacturers have increased the compression ratio of engines withPCCs, as the very lean mixtures enable a more-efficient highercompression ratio to be used, compared with engines operated with aricher air-fuel mixture.

There are a number of natural gas engines currently in service havingPCCs with the separate gas admission valves. In these engines, theadditional apparatus required for the PCC design makes the engine morecomplex to optimize and more subject to malfunction than the openchamber engine with a standard spark plug. Hence, there is a need for atrouble-free implementation for engines with PCCs. For existing engineswith PCCs and the associated apparatus, the innovations described in thefollowing description can provide benefits to the users and owners ofsuch engines.

Accordingly, systems and methods that enable emission reduction innatural gas engines remain highly desirable.

BRIEF DESCRIPTION OF THE DRAWINGS

Further features and advantages of the present disclosure will becomeapparent from the following detailed description, taken in combinationwith the appended drawings, in which:

FIG. 1 shows a representation of an engine fuel system with PCC;

FIG. 2 shows a representation of an engine head with PCC;

FIG. 3 shows a modified PCC engine head with a chambered spark plug;

FIG. 4 shows a plug carrier and modified extension;

FIG. 5 shows a sectioned view of the plug carrier and modifiedextension;

FIG. 6 shows a representation of an engine management system;

FIG. 7 shows a method of ignition timing;

FIG. 8 a representation of determining advance or retard determination;and

FIG. 9 shows a comparison of NOx emission between a PCC and convertedPCC engine.

It will be noted that throughout the appended drawings, like featuresare identified by like reference numerals.

DETAILED DESCRIPTION

In accordance with an aspect of the present disclosure there is provideda method of modifying a pre-combustion chamber engine to reduce NOxemissions, the method comprising: removing pre-combustion chambercylinder heads; disabling an admission valve assembly of thepre-combustion chamber engine; inserting a modified cylinder head forreceiving a pre-chambered sparkplug in an extension tube; connecting thesparkplug to ignition terminals; connecting a detonation detectionsystem to the engine; and modifying ignition timing of thepre-combustion chamber engine based upon signals received from thedetonation detection system.

In accordance with an aspect of the method the ignition timing isdetermined by calculating Output %=I_(r)(FDen)+I_(r)(F_(s1))+Max[I_(r)(AMP), I_(r)(AMT), I_(r)(Fuel), I_(r)(Load), I_(r)(RPM),I_(r)(Det)]*[100−I_(r)(FDen)+I_(r)(F_(s1))] where I_(r)(AMP) is acalculated ignition retard % for an air manifold pressure; I_(r)(AMT) isa calculated ignition retard % for an air manifold temperature;I_(r)(Fuel) is a calculated ignition retard % for fuel flow; I_(r)(Load)is a calculated ignition retard % for load; I_(r)(RPM) is a calculatedignition retard % for RPM; I_(r)(FDen) is a calculated ignition retard %for density; I_(r)(F_(s1)) is a calculated ignition retard % forsupplemental gas flow; and I_(r)(Det) is a calculated ignition retard %for detonation.

In accordance with an aspect of the method the Output % is a differencebetween a desired Output % and the Output % according to actual timingvalue.

In accordance with an aspect of the method determining an Output % errorwherein the Output % error is a difference between an actual output %and a desired output %.

In accordance with an aspect of the method an Output % error is comparedto a specified minimum error for retard and a maximum error for advance.

In accordance with an aspect of the method if the Output % error becomestoo large, then the Output % is retarded at a specified rate until theOutput % error drops below a minimum error for retard.

In accordance with an aspect of the method the Output % error becomesless than the maximum % error for advance the Output % is advanced.

In accordance with an aspect of the method the ignition timing ismodified until a stable condition is reached where neither advance norretard occurs unless one of an operational parameter changessufficiently.

In accordance with an aspect of the method a Waukesha™ VHP GL enginecylinder heads are replaced by a non-PCC cylinder heads from a Waukesha™VHP GSI engine.

In accordance with an aspect of the present disclosure there is providedan engine management system comprising: an input/output (I/O) interfacecoupled to one or more sensors of a natural gas engine having chamberedsparkplugs; a processor coupled to the I/O interface; a memorycontaining instructions which when executed by the processor for:receiving sensor data from the engine through the I/O interface;receiving a detonation signal from a detonation detection system fromthe engine; determining an output % from the sensor data; and generatinga timing signal to advance or retard ignition timing to adjust thedetonation signal to achieve a desired output %.

In accordance with an aspect of the engine management system theignition timing is determined by calculating Output%=I_(r)(FDen)+I_(r)(F_(s1))+Max [I_(r)(AMP), I_(r)(AMT), I_(r)(Fuel),I_(r)(Load), I_(r)(RPM), I_(r)(Det)]*[100−I_(r)(FDen)+I_(r)(F_(s1))]where I_(r)(AMP) is a calculated ignition retard % for an air manifoldpressure; I_(r)(AMT) is a calculated ignition retard % for an airmanifold temperature; I_(r)(Fuel) is a calculated ignition retard % forfuel flow; I_(r)(Load) is a calculated ignition retard % for load;I_(r)(RPM) is a calculated ignition retard % for RPM; I_(r)(FDen) is acalculated ignition retard % for density; I_(r)(F_(s1)) is a calculatedignition retard % for supplemental gas flow; and I_(r)(Det) is acalculated ignition retard % for detonation.

In accordance with an aspect of the engine management system the Output% is a difference between the desired Output % and the Output %according to actual timing value.

In accordance with an aspect of the engine management system thedetermining an Output % error wherein the Output % error is a differencebetween an actual output % and the desired output %.

In accordance with an aspect of the engine management system an Output %error is compared to a specified minimum error for retard and a maximumerror for advance.

In accordance with an aspect of the engine management system if theOutput % error becomes too large, then the Output % is retarded at aspecified rate until the Output % error drops below a minimum error forretard.

In accordance with an aspect of the engine management system the Output% error becomes less than the maximum % error for advance the Output %is advanced.

In accordance with an aspect of the engine management system theignition timing is modified until a stable condition is reached whereneither advance nor retard occurs unless one of an operational parameterchanges sufficiently.

In accordance with an aspect of the engine management system an engineair-fuel ratio and ignition timing is different compared to that of anoriginal equipment manufacturers recommendations.

In accordance with an aspect of the engine management system a Waukesha™VHP GL engine cylinder heads are replaced by non-PCC cylinder heads froma Waukesha™ VHP GSI engine.

In accordance with an aspect of the present disclosure there is provideda method of engine management in a natural gas engine having a chamberedsparkplug, the method comprising: receiving sensor data from the engine;receiving a detonation signal from the engine from a detonationdetection system; determining an output % from the sensor data and thedetonation signal; and generating a timing signal to advance or retardignition timing to adjust the detonation signal to achieve a desiredoutput %.

In accordance with an aspect of the method the ignition timing isdetermined by calculating Output %=I_(r)(FDen)+I_(r)(F_(s1))+Max[I_(r)(AMP), I_(r)(AMT), I_(r)(Fuel), I_(r)(Load), I_(r)(RPM),I_(r)(Det)]*[100−I_(r)(FDen)+I_(r)(F_(s1))] where I_(r)(AMP) is acalculated ignition retard % for an air manifold pressure; I_(r)(AMT) isa calculated ignition retard % for an air manifold temperature;I_(r)(Fuel) is a calculated ignition retard % for fuel flow; I_(r)(Load)is a calculated ignition retard % for load; I_(r)(RPM) is a calculatedignition retard % for RPM; I_(r)(FDen) is a calculated ignition retard %for density; I_(r)(F_(s1)) is a calculated ignition retard % forsupplemental gas flow; and I_(r)(Det) is a calculated ignition retard %for detonation.

In accordance with an aspect of the method the Output % is a differencebetween the desired Output % and the Output % according to actual timingvalue.

In accordance with an aspect of the method determining an Output % errorwherein the Output % error is a difference between an actual output %and the desired output %.

In accordance with an aspect of the method an Output % error is comparedto a specified minimum error for retard and a maximum error for advance.

In accordance with an aspect of the method the Output % error becomestoo large, then the Output % is retarded at a specified rate until theOutput % error drops below a minimum error for retard.

In accordance with an aspect of the method the Output % error becomesless than the maximum % error for advance the Output % is advanced.

In accordance with an aspect of the method the ignition timing ismodified until a stable condition is reached where neither advance norretard occurs unless one of an operational parameter changessufficiently.

In accordance with an aspect of the method an engine air-fuel ratio andignition timing is different compared to that of an original equipmentmanufacturers recommendations.

In accordance with an aspect of the method a Waukesha™ VHP GL enginecylinder heads are replaced by non-PCC cylinder heads from a Waukesha™VHP GSI engine.

In accordance with an aspect of the present disclosure there is provideda chambered sparkplug carrier for a natural gas engine, the chamberedsparkplug carrier comprising: an circular shaft for receiving achambered sparkplug within a first end of the shaft, the chamberedsparkplug engaged with the shaft by threads at a tip of the first endwherein a combustion chamber of the chambered sparkplug extends beyondthe tip of the first end; an internal extension coupling the chamberedsparkplug to an ignition system at a second end of the shaft; andwherein the chambered sparkplug carrier is used in a pre-combustionchamber engine to replace the pre-combustion chamber with the chambersparkplug carrier.

In accordance with an aspect of the chambered sparkplug the ignitiontiming of the engine is modified to be advanced or retarded to achieve adesired output % of the engine.

In accordance with an aspect of the chambered sparkplug the ignitiontiming of the is modified by engine management system by receiving adetonation signal from the natural gas engine.

In accordance with an aspect of the chambered sparkplug furthercomprises outer threads on the circular shaft for engaging the cylinderhead.

In accordance with an aspect of the chambered sparkplug furthercomprises bolts for engaging the cylinder head.

In accordance with an aspect of the chambered sparkplug wherein aWaukesha™ VHP GL engine cylinder heads are replaced by non-PCC cylinderheads from a Waukesha™ VHP GSI engine.

Embodiments are described below, by way of example only, with referenceto FIGS. 1-9. The schematic for an engine 100 with a pre-combustionchamber (PCC) is shown in FIG. 1. Intake air to the engine passesthrough an air cleaner 102, a turbo charger 104 and intercooler 106before entering a carburetor 108. An engine cylinder 120 receivesair-fuel mixture from carburetor 108 where the fuel gas is suppliedthrough a biased fuel pressure regulator 110. The PCC 122, shown by acircle at the top of the main combustion chamber 124 of an enginecylinder 120 has small holes to permit the flow of gases into and out ofthe main combustion chamber 124. In the operation of a four-stroke cycleengine during the downward intake stroke while a very lean air-fuelmixture enters the main chamber 124 through the open intake valve, fuelto the PCC is supplied through a check valve 114 and a biased fuelpressure regulator 112. During the compression stroke the very leanair-fuel mixture from the main chamber 124 flows into the PCC 122. Thecheck valve 114 prevents the previously added fuel from being expelled.A spark plug (not shown) in the PCC ignites the richer air-fuel mixturein the PCC 122. The ensuing combustion causes the gases to reach ahigher pressure than is present in the main chamber 124. These hotburning gases consequently flow out into the main chamber 124 ignitingthe very lean air-fuel mixture in the main chamber 124. In the powerstroke force is transmitted to the engine crankshaft (not shown). In theexhaust stroke the exhaust gases from the PCC 122 and the main chamber124 are expelled to the engine exhaust system through the main chamber124 exhaust valve. The whole sequence of operation is then repeated.FIG. 1 is shown for illustrative purposes, it should be understood thatthere are a variety of possible PCC fuel or air-fuel deliveryarrangements. In addition supplementary gas source may be utilized topower the engine. The supplementary gas can be provided by captured ventgas in oil production and storage and used by the engine to reduce ventgas emissions by combusting excess gas. The supplemental gas flowdisplaces a portion of the main fuel flow requirement of the engine andmay be of a different composition than the main fuel source.

A cross-section of an engine head showing the PCC and the gas admissionvalve is shown in FIG. 2. The PCC 122 is positioned in the main chamber124 of the cylinder head 220. During the intake stroke, when the leanair-fuel mixture is drawn into the main chamber 124, the PCC admissionvalve 230 opens to enable some fuel to enter the PCC 122. During thecompression stroke, the PCC admission valve 230 closes and some of thelean air-fuel mixture from the main chamber 124 enters the PCC 122 tomix with the fuel previously admitted. A few degrees before top-deadcenter (TDC); the spark discharge from the spark plug 222 ignites themixture in the PCC 122. The hot, burning gases expand into the mainchamber 124, igniting the lean mixture through openings 226. During theexpansion stroke and subsequent exhaust stroke the gas admission valve230 remains closed to prevent the hot combustion gases from flowing backto the PCC 122 air-fuel mixing apparatus.

Referring to FIG. 3, a modified PCC engine cylinder is shown where thePCC is replaced with a chambered sparkplug. To extend the lean limit thechambered sparkplug can be utilized having a small chamber around thenormal sparkplug electrodes which serves as a region where conditionsfor igniting a lean air-fuel mixture are optimized. Such chamberedsparkplugs are available commercially from Altronic™ and Multitorch™.Use of these chambered sparkplugs in combination with leaner operationcan be effective in reducing NOx emissions from SI-RICEs. A sparkplugcarrier can be used to replace the original PCC and spark plug carrieritems with a single plug carrier that allows the chambered spark plug toextend into the combustion chamber. In FIG. 3 the PCC is replaced withthe chambered spark plug 322 provided inside the carrier 320 inserted inthe PCC cylinder head 220. The modified spark plug carrier 320 is usedto hold the chambered spark plug 322 in place and position the ignitionchamber 324 in the main chamber 124. The chamber 324 of the chamberspark plug 322 is filled through the orifices 326 during the compressionstroke with the same lean mixture as that in the main chamber 124. Thevolume of the chamber 324 is a much smaller fraction of the combustionchamber than the typical PCCs 122. The PCC admission valve 230 in theigniter sleeve 210 is bypassed with the installation of the chamberedspark plug 322 and spark plug carrier 320.

By replacing the PCC 122 and its sparkplug 222 with a modified sparkplugcarrier 320 and a chambered sparkplug 322, the need for a separate PCC,gas admission valve 230, and apparatus for the PCC can be eliminated.The sparkplug carrier 320 is shown in FIG. 4. FIG. 5 shows a sectionedview of the plug carrier 320. The chambered spark plug 322 is engaged tothe sparkplug carrier 320 by threads 502. An extender 530 inside thespark plug carrier 320 connects to the coil ignition terminals or leads.O-ring grooves 510 may be provided are on the outside of the plugcarrier 320 to create a seal with the cylinder head 220 if a seal if thesleeve 210 seals with the cylinder head. Cylinder head threads 512 areprovided to retain the sparkplug carrier 320 within the cylinder head220 is a modified igniter sleeve 210 is utilized with receiving threads.Alternatively, the sparkplug carrier 320 may be a bolt-in to replace thePCC and not require cylinder thread heads 512.

Referring to FIG. 6, the engine 650 is controlled by an engine managmentsystem (EMS) 610. The change in combustion conditions between theoriginal engine and the modified engine with the single plug carrier andchamber spark plug requires a modified ignition timing advance andretard algorithm that includes an input from a detonation detectionsystem 660 in addition engine sensors from speed, temperature etc. Thedetonation detection system 660 can be added as part of the retrofitapplication of PCC engine to chamber sparkplug carrier system. The EMS610 changes provides a modified ignition timing advance and retardalgorithm. The EMS 610 comprises a processor 612 and memory 614containing instructions which when executed by the processor are forcontrolling the ignition of the engine. Input/Output (I/O) interface 616can receive sensor data or signals from the engine such as detonationdetection, air manifold pressure, air manifold temperature, engine load,rotation per minute (RPM), fuel flow rate, and fuel density and providemodified ignition timing to control the modified engine 650 withchambered sparkplugs.

For the high compression engine where detonation is more likely comparedto the lower compression engine the inclusion of detonation with theother items which may control engine timing is important to avoidpremature cylinder failure. Due to the need to have ignition advance andlean operation under load without excessive intake temperatures, theignition control was integrated with the air control to optimize engineoperation with the available turbocharger output. The modified engineignition control enables starting and warm-up with retarded ignitiontiming and then slowly advances the ignition timing to a maximumdepending on the availability of sufficient cool air.

Normally the spark ignition timing is described in degrees beforetop-dead-centre (TDC). A timing advance means that the spark ignitionoccurs earlier than the previous reference timing, while a timing retardmeans the spark ignition occurs later than the previous referencetiming.

With reference to the method shown in FIG. 7, ignition advance operatesby receiving sensor data and providing ignition timing for the naturalgas engine. The desired ignition retard from the maximum allowed advanceis expressed as an output percentage of the difference in degreesbetween the advance and retard angles. Each parameter for which thetiming can be adjusted is included. The formula for the contribution ofeach parameter to the ignition retard effect is specific to each enginetype. The final output percentage is calculated according to the formulabelow. The output percentage is then converted to an electrical orsoftware value appropriate to control the spark ignition timing.

Output %=I _(r)(FDen)+I _(r)(F _(s1))+Max [I _(r)(AMP), I _(r)(AMT), I_(r)(Fuel), I _(r)(Load), I _(r)(RPM)]*[100−I _(r)(FDen)+I _(r)(F_(s1))]

Where I_(r)(AMP) is the calculated ignition retard % for the airmanifold pressure (720)

I_(r)(AMT) is the calculated ignition retard % for the air manifoldtemperature (722)

I_(r)(Fuel) is the calculated ignition retard % for fuel flow (724)

I_(r)(Load) is the calculated ignition retard % for load (726)

I_(r)(RPM) is the calculated ignition retard % for RPM (728)

-   I_(r)(FDen) is the calculated ignition retard % for density (732)-   I_(r)(F_(s1)) is the calculated ignition retard % for supplemental    gas flow (734).

For a high compression engine detonation, the uncontrolled initiation ofcombustion ignition, is a known problem. The original detonation systemacts on the ignition timing control to retard the ignition timing in astep change. This is incompatible with the previously developed ignitioncontrol strategy. For the incorporation of the detonation signal, ratesof timing advance and retard were used and incorporated into the aboveexpression for ignition output. A detonation input is added to the aboveexpression as shown to calculate the maximum output percentage (702).The output % can then be calculated (702) according to:

Output %=I _(r)(FDen)+I _(r)(F _(s1))+Max [I _(r)(AMP), I _(r)(AMT), I_(r)(Fuel), I _(r)(Load), I _(r)(RPM), I _(r)(Det)]*[100−I _(r)(FDen)+I_(r)(F _(s1))]

where I_(r)(Det) is the calculated ignition retard % for detonation(730)

-   The ignition timing angle is then Ign−I_(ret)*Output %/100-   Where Ign is the ignition timing angle BTDC    -   I_(ret) is the maximum ignition retard amount

Also with reference to FIG. 8, an Output % error is calculated 802,which is the difference between the desired Output % and the Output %according to actual timing value. The Output % error signal 800 iscompared to the specified minimum error 804 for retard and a maximumerror 806 for advance (706). If the error signal becomes too large (YESat 708), then the Output % is retarded at the specified rate (712) ofretard until the error drops below the minimum error for retard.Similarly, if the error signal becomes less than the maximum errorpercentage (YES at 710) for advance the Output % is advanced (714).Typically the rate of retard is greater than the rate of advance.Eventually the ignition timing reaches a stable condition where neitheradvance nor retard occurs unless one of the operational parameterschanges sufficiently.

Alternatively, a cylinder head design with a PCC can be replaced by anon-PCC head design for the same engine block but with a chamberedsparkplug in place of the normal spark plug if the replacement head issuitable for the higher pressure associated with the higher compressionratio. This can remove the need for a modified sparkplug carrier howeverthe ignition timing method of FIG. 7 is still required.

Both designs enable NOx emission concentration limits achievable withthe engine heads with PCCs with or without separate fuel deliverysystems to be met by the chambered sparkplug either with a modifiedsparkplug carrier or with a non-PCC head. It is recognized that, toachieve the desired NOx emission limits, the engine air-fuel ratio andignition timing is different compared to that of the original equipmentmanufacturers' recommendations.

FIG. 9 is a graph 900 showing comparison of NOx emissions where thecylinder heads for a Waukesha™ VHP GL engine (GL NOx emissions), whichhas a PCC as shown in FIG. 2, were replaced by the non-PCC cylinderheads from a Waukesha™ VHP GSI engine and chambered sparkplugs(converted GL NOx emissions). The Waukesha™ VHP GSI heads do not have aPCC or a gas admission valve. For this engine type, carbon moNOxide (CO)and total hydrocarbon (THC) emissions reductions can also be expectedbecause there are no high CO concentrations from the PCC and there arefewer crevice volumes and quenching surfaces with the GSI cylinder headand the chambered sparkplug, compared to the GL cylinder head.

The result of the innovative plug carrier and ignition control is thatregulated exhaust emissions are either reduced or not increased with asimpler arrangement that is less prone to mal-adjustment or malfunction.Furthermore, if the original engine with the heads modified for PCCs hasa modification for a higher compression ratio, the higher compressionfeature can be retained with the innovation.

Each element in the embodiments of the present disclosure may beimplemented as hardware, software/program, or any combination thereof.Software codes, either in its entirety or a part thereof, may be storedin a computer readable medium or memory (e.g., as a ROM, for example anon-volatile memory such as flash memory, CD ROM, DVD ROM, Blu-ray™, asemiconductor ROM, USB, or a magnetic recording medium, for example ahard disk). The program may be in the form of source code, object code,a code intermediate source and object code such as partially compiledform, or in any other form.

It would be appreciated by one of ordinary skill in the art that thesystem and components shown in FIGS. 1-9 may include components notshown in the drawings. For simplicity and clarity of the illustration,elements in the figures are not necessarily to scale, are only schematicand are non-limiting of the elements structures. It will be apparent topersons skilled in the art that a number of variations and modificationscan be made without departing from the scope of the invention as definedin the claims.

What is claimed is:
 1. A chambered sparkplug carrier for a natural gasengine, the chambered sparkplug carrier comprising: a circular shaft forreceiving a chambered sparkplug within a first end of the shaft, thechambered sparkplug engaged with the shaft by threads at a tip of thefirst end wherein a combustion chamber of the chambered sparkplugextends beyond the tip of the first end; an internal extension couplingthe chambered sparkplug to an ignition system at a second end of theshaft; and wherein the chambered sparkplug carrier is used in apre-combustion chamber engine to replace the pre-combustion chamber withthe chamber sparkplug carrier.
 2. The chambered sparkplug carrier ofclaim 1, wherein the sparkplug carrier further comprises outer threadson the circular shaft for engaging the cylinder head.
 3. The chamberedsparkplug carrier of claim 1, wherein the sparkplug carrier furthercomprises bolts for engaging the cylinder head.
 4. The chamberedsparkplug carrier of claim 3, wherein Waukesha™ VHP GL engine cylinderheads are replaced by non-PCC cylinder heads from a Waukesha™ VHP GSIengine.